ES2329095T3 - HEAT EXCHANGER WITH A COLD ACCUMULATOR. - Google Patents

Abstract

Heat exchanger, in particular an evaporator (1), in particular for an air-conditioning installation of motor vehicles, with a plurality of pipes that conduct a cooling medium, located next to each other, and with at least one cold accumulator ( 4), in which a cold storage medium is provided, characterized in that the evaporator (1) has two zones (1 '' and 1 '' '') arranged parallel to each other and extending along the entire the width, the first zone (1 '') corresponding to its structure corresponding to a conventional evaporator, the cold accumulator (4) being arranged in a second independent zone (1 '' '), which can be crossed by less by a part of the cooling medium stream, which also crosses at least a part of the first zone (1 '') and the first and second zones being connected to each other by at least one spill opening (13 ).

Description

Heat exchanger with an accumulator of cold.

The present invention relates to a heat exchanger, in particular for an installation of air conditioning of motor vehicles, with cold storage, according to the preamble of claim 1. The US document 2003 / 041610A1 unveils a heat exchanger of this kind.

A goal of vehicle manufacturers Automobiles is to reduce the fuel consumption of the vehicle. A measure for the reduction of fuel consumption is the disconnection of the engine during a temporary stop, for example during stop at a traffic light. This temporary disconnection of the motor is also called "Idle-Stop" operation. This measure is used in current low-powered motor vehicles. consumption as, for example, the so-called three-liter vehicle. In vehicles with operating mode Idle-Stop the engine is disconnected, in traffic through the interior of the city, approximately between 25 and 30% of the time of the march.

This is one reason why vehicles these types are not frequently equipped with a installation of air conditioning, because during engine shutdown you cannot also drive a compressor necessary for the installation of air conditioning, so that in operation Idle-Stop an air conditioning installation cannot provide the necessary cooling capacity. The problem is resolves in part also because when the installation of air conditioning is connected the engine continues to run for the stop, which results in however a fuel consumption higher.

In document DE 101 56 944 A1, it is given to know an air conditioning system for a motor vehicle with a compressor and an evaporator arranged in a medium circuit refrigerant for cooling air conditioning for the cabin, which presents a second evaporator for air cooling, which additionally contains a medium cold accumulator, being able to conduct the air to be condition, optionally, through each evaporator, individually or through both evaporators, together. From according to an alternative embodiment in the place of second evaporator the evaporator is formed in such a way that It has two partial zones and contains, in one of the two zones partial, a means of accumulating cold, being able to conduct the air to be conditioned, optionally, through each evaporator, individually, or through both evaporators, jointly. At the same time the tubes, in which the medium refrigerant circulates through the evaporator, may be formed as a multi-channel tube, with one or several channels filled With the cold storage medium.

Starting from this state of the art the invention poses the problem of providing an exchanger of improved heat. This problem is solved by heat exchanger with the characteristics of the claim 1. Advantageous structuring is the objective of the subordinate claims.

According to the invention, a heat exchanger, in particular an evaporator for a installation of air conditioning of motor vehicles for the cooling of the air to be conditioned for the cabin, with a large number of pipes that conduct a cooling medium, located next to each other, and with at least one accumulator of cold, in which a cold storage medium is provided. The same time the evaporator has two zones, arranged parallel between yes and that run along the entire width, the first zone corresponding to its structure corresponding to a conventional evaporator, the cold store being arranged in a second independent zone, which can be crossed by less for a part of the coolant stream, which it also crosses at least part of the first zone, and the first and second zones being connected to each other by at least one spill opening. Through the opening of spill at least a partial stream of medium is spilled refrigerant from one zone to the other zone, that is, in both zones circulates cooling medium. Between the first and / or tubes of the second heat exchanger zones may be arranged wavy nerves or other elements that extend the heat exchange surface. Thanks to the first zone corresponds essentially to a conventional heat exchanger you can continue using existing tools, you have to acquire only the tools for the second zone and for the realization of the spill opening (s). The second zone can be adapted - for the first structured zone in correspondence with the constructive form used so far - of relatively simple way to existing building space and to refrigeration needs It is needed additionally only one organ of expansion.

Based on the modular structure you can designate an evaporator formed in this way also as "Add-on" accumulator evaporator, that is, the basic form of the evaporator in principle is added a correspondingly formed cooling module.

Preferably precisely two are provided spill openings, though - in the case of a supply by separated from cooling medium - can also be provided only a spill opening. It is also possible a great number of spill openings, through which you can spill cooling medium from the first zone to the Second zone and vice versa.

In at least one cold storage element at least one tube that conducts a means is arranged refrigerant. At the same time, the cold accumulator elements they can be connected to each other, especially through so minus a collecting container.

In the case of a tube arrangement that conducts a cooling medium in the cold accumulator element may be inserted in the cold storage element filled with cold storage medium or be formed, however, directly inside, surrounding the cold storage medium preferably the cooling medium everywhere, especially provided a tube-in-tube arrangement.

The cold storage element may be also formed by a tube with a U-shaped cross section, especially with several cameras. At the same time they correspond preferably the internal dimensions of the accumulator element from cold to the outer dimensions of the tube that conducts a medium refrigerant in the corresponding area, so that the tubes They are in superficial contact with each other. It is possible also a structuring of a piece, for example formed by a tube correspondingly extruded with at least two channels.

The tube that conducts a cooling medium and the cold storage medium is formed, in the case of an arrangement  completely inside the cold storage element, preferably as a flat double-walled tube, the cooling medium in the central area and the cold storage medium in the outer zone. According to another preferred embodiment, the double wall flat tube has nerves, which connect the flat tube located outside with the one located inside. Thanks to the cold accumulator having direct contact with the air is a very good dynamic during the transmission of heat, so that if necessary, that is in the Idle-Stop operation, is located immediately available all the power refrigerating

The tube containing the cold storage medium it cannot completely surround the tube that conducts the medium either refrigerant. At the same time, they are preferably surrounded exactly three sides of the tube that conducts a cooling medium by the tube that contains half cold accumulator. The tube that contains the cold storage medium can be formed to it time with a U-shaped cross section and surround the tube which conducts a cooling medium, preferably being a flat tube, in part, that is along a part of its perimeter, with most of the tube leading a cooling medium inside the tube containing the medium cold storage

The pipes that conduct a cooling medium of the second zone preferably ends in a collecting vessel, which is formed separately from and only with one or more spill openings with a collecting container of the first zone. This also allows a subsequent retrofitting of the heat exchanger with a cold store, especially however, the first zones may be formed - without having account for spill openings - immediately, as in the case of conventional heat exchangers, so that can reduce manufacturing costs, as a result of a large number of equal parts and tools, for a large part of the components. In addition, the two zones can be mounted separately and can then be connected to each other.

The tubes or respectively channels that conduct cold accumulator media end up in a container collector of cold storage medium, through which they protrude tubes or respectively conductive channels of cooling medium, which end up in a separate collecting container. This enables a common filling of the cold accumulator elements individual with the cold storage medium, so that it is a simple and fast filling of the tubes is possible or respectively channels that lead half cold accumulator. In addition, the assembly it can be simplified preferably by structuring a piece of the cold store in the case of a formation separate from the pipes that conduct a cooling medium and from the cold storage elements. In this way, it can be provided also a compensation space for volume variations of the cooling medium, especially conditioned by temperature. This also enables a compact constructive form of the second zone

The first zone preferably has a number of blocks, which can be traversed in the middle refrigerant in different directions, in the direction of your width adjacent to the second zone, and the second zone at least a block, especially a number of blocks that can be crossed by the cooling medium in different directions. To the same time, the number and / or width is preferably differentiated of the individual blocks in the direction of the width of the evaporator in the first zone and in the second zone. The first zone preferably, directly adjacent to the second zone, two to four, especially three blocks, and the second zone one to six blocks, especially two to four blocks.

The rows of flat tubes of the first zone and from the second zone they are preferably aligned with each other, being able to be arranged however also behind each flat tube n-th, especially every second or third, of the first zone, a flat tube of the second zone, so that the resistance to air circulation is small, although the rows of flat tubes they can also be arranged irregularly or displaced (e.g. in the central position in the interstitium), or the elements cold accumulators, with the tubes that conduct a medium refrigerant arranged inside, may be arranged rotated with respect to the other flat tubes of the evaporator. He number and shape of the flat tubes of the second zone can be choose in correspondence with the desired amount of heat in the case of one for the motor vehicle.

The second evaporator zone is arranged, preferably seen in the normal direction of movement of the air, towards the first evaporator zone, especially directly in the zone of connection with the evaporator, but it is possible without however also an arrangement before the evaporator or something distanced from the evaporator in a second evaporator piece, in Smaller particular. In particular, in the case of a provision  distanced from the evaporator (main) the collector size with cold store in correspondence with the available construction space and / or the requirements. Is especially advantageous that the existing evaporator does not have to be modified or should be irrelevant, so that it is a relatively simple integration of the accumulator of cold in existing systems. Existing tools do not have to be modified (or should only be so Irrelevant). You only need to acquire the tools for evaporator cold accumulator zone, which is added.

In the case of the tubes that are crossed by the cooling medium, they are preferably welded, folded, deep-drawn flat tubes from discs or extruded, which can be formed both rounded and angular. However, for example, oval tubes or round section tubes can also be used. As materials, aluminum and aluminum alloys are especially considered, although it is also possible to use suitable discretionary materials that conduct the
hot.

The cold storage is done, preferably, in aluminum, especially aluminum coated by inside and / or outside (an aluminum should also be understood as a aluminum alloy), also copper, an alloy of copper-zinc, synthetic resin or plastic. A Aluminum container has the advantage that it can be welded without problems with the remaining parts of the evaporator. At the same time it is preferably an extruded flat tube, which has a large number of channels, containing a part of the channels the cold storage medium and another cooling medium. The structuring can be however also in several pieces.

In the case of the latent medium or accumulator it is preferably a PCM (phase change material) material that contains or is formed by means that melt so congruent, especially decanol, tetra-, penta- or hexadecane, LiClO 3 3H 2 O, aqueous saline solutions or hydrates organic In the storage medium may also be provided germ trainers, which accelerate the formation of crystals.

The phase change temperature of the medium accumulator is preferably in a range between 0 ° C and 30 ° C, preferably between 1 ° C and 20 ° C, in particular between 2 ° C and 15 ° C, particularly preferably between 4 ° C and 12 ° C.

Inside the cold storage element - regardless of whether it surrounds completely or only partially the tube that conducts a cooling medium - they can be provided with additional pieces, such as nerve plates, made preferably in aluminum, although others are also suitable metals or plastics, or other added parts of turbulence, such as nonwoven materials or knitwear, for example of plastic or metal, or foams, for example metal foams or plastic foams. The added pieces serve to improve the heat exchange as well as for surface increase interior in order to accelerate the formation of crystals in the half accumulator

The passage through both zones takes place, preferably, in series, so that it is intended only an organ of expansion for both zones. At the same time the entrance of cooling medium is preferably provided in the manifold from the first zone.

The heat exchanger preferably has The following dimensions (with respect to dimensions are Refer to Figures 8 and 9):

The total depth T of the exchanger of heat is preferably between 23 and 200 mm, in particularly between 35 and 80 mm, especially preferably 60 +/- 10 mm.

The construction depth T 'is preferably between 20 and 150 mm, in particular between 25 and
90 mm The construction depths T1 and T2 of the flat tubes of the evaporator in the zone without cold accumulator correspond in general to each other (symmetrical structuring of this zone of the evaporator).

The widths b1 and b2 of the flat tubes of the evaporator in the area without cold accumulator correspond preferably with each other, aligning preferably in each case a flat tube of one row with a flat tube of the other row. The widths b1 and b2 preferably measure 0.8 to 4 mm, in particular 1.3 to 3.5 mm

The transverse step q1 of the first row of flat tubes preferably measures between 4 and 20 mm, in particular preferably between 5 and 13 mm. It corresponds preferably to the step cross section of the second row of flat evaporator tubes.

The height of the wavy nerve of the first row of flat tubes measures, therefore, preferably between 3 and 18 mm, in particular between 4 and 10 mm. It corresponds preferably to the height of the wavy nerve of the second row of flat tubes of the evaporator.

The evaporator in the cold storage area It has flat tubes, which contain the storage medium of cold in the external cold storage media channels, with widths b3 preferably between 2.0 and 10.0 mm, in particular between 3.0 and 8.0 mm. The width b4 of the flat tubes arranged inside, in whose cooling medium channels the cooling medium circulates, preferably measures between 0.6 and 2.5 mm, in particular between 0.9 and 1.5 mm.

T3 construction depth of pipes Evaporator planes in the area with cold accumulator measures, preferably, between 5 and 70 mm, in particular, preferably between 10 and 30 mm.

The transverse passage q3 of the flat tubes of the evaporator in the area with a cold accumulator preferably measures a multiple of q1, in order to keep this small circulating air pressure drop, although it may correspond also to q1. Values two and three are especially preferred.

The height H1 of the medium collecting container cold accumulator preferably measures between 3 and 25 mm, in particular between 3 and 15 mm, although it is preferably so small as possible, in order to save constructive space and keep the section that can be traversed by air as much big possible.

The invention is explained below in detail from an exemplary embodiment with variants, partially referring to the drawing, in the that:

Fig. 1 shows a perspective view of a heat exchanger with manifold according to a first example of embodiment,

Fig. 2 shows a side view of the heat exchanger of Fig. 1,

Fig. 3 shows a perspective view, a trimming mode of the heat exchanger of Fig. 1 with the collecting box and collecting tube removed,

Fig. 4 shows another perspective view of a zone of the heat exchanger of Fig. 1 with container and the tube collectors open laterally,

Fig. 5 shows a sectioned side view of the heat exchanger of Fig. 1,

Fig. 6 shows a detailed view of a spill opening,

Fig. 7 shows a detail view section of the heat exchanger of Fig. 1 in the area of cold accumulator,

Fig. 8 shows a cross section to through the heat exchanger of Fig. 1,

Fig. 9 shows a section through the lower zone of the heat exchanger of Fig. 1,

Fig. 10 shows a perspective view of the heat exchanger of Fig. 1 with schematic representation of the circulation path of the cooling medium,

Fig. 11 shows a sectional representation schematic of the heat exchanger of Fig. 1 for the illustration of the circulation path of the cooling medium,

Fig. 12 shows a schematic side view from the area of the heat exchanger with the cold accumulator of Fig. 1 for illustration of the circulation path of the medium refrigerant,

Figs. 13a, b show some representations schematics of the circulation path of the cooling medium according to a first variant,

Figs. 14a, b show some representations schematics of the circulation path of the cooling medium according to a second variant,

Figs. 15a, b show some representations schematics of the circulation path of the cooling medium according to a third variant,

Figs. 16a, b show some representations schematics of the circulation path of the cooling medium according to a fourth variant,

Figs. 17a, b show some representations schematics of the circulation path of the cooling medium according to a fifth variant, and

Figs. 18a, b show representations schematics of the circulation path of the cooling medium according to a sixth variant.

A vehicle air conditioning installation cars for regulating the temperature of the passenger compartment of motor vehicle with a refrigerant medium circuit (in the It presents case R134a, although it can also be used for example CO 2 or other cooling medium), of which they are represented only evaporator 1, with injection tube 2 and tube suction 3, presents, to also provide during a stop  of the engine for at least a short time a sufficient cooling power, a cold store 4, formed by a large number of cold storage elements 5, in the present case twenty-two, which are filled with a medium cold storage The cold storage elements 5 are made of aluminum, by means of flat tube areas 6 specially structured, about which it will become at one point later. As a cold storage medium, this is the case decanol. Alternatively they are suitable, for example, also tetra-, penta- or hexadecane.

The direction of normal air circulation is indicated by arrows in Figures 1 and 2. Evaporator 1 it presents in the greater part, of the side of entrance of air, a zone 1 ' with a structure, which corresponds to that of an evaporator conventional, with two rows of flat tubes 7 and corrugated ribs 8 arranged among them. The flat tubes 7 end in each case in a collecting container 9. As shown in Figures 1 and 2, the cooling medium enters the narrow side of the container upper manifold 9, on the air outlet side, in the evaporator 1 and leaves it, on the same narrow side, in the area of air inlet of the collecting vessel 9.

The other zone of evaporator 1, that is the zone of 1 '' cold accumulator, which in principle is formed separately as an independent zone of evaporator 1 and in which they are provided the cold accumulator elements 5, is formed by the smaller part, on the air outlet side, of the evaporator 1.

The flat tubes of cold storage 6 in the 1 '' cold storage zone zone and flat tubes 7 conventional in zone 1 ', as it is clear in particular from the Fig. 8, are arranged in such a way that in each case it is arranged with the first, third, fifth, etc. flat tube 7, aligned in each case with the same in the direction of air circulation, a flat cold accumulator tube 6.

Since the intermediate spaces between the flat cold accumulator tubes 6, which are presently case are narrower in the direction of air circulation, but that transversely to it are formed wider than the tubes planes 7, which are relatively wide due to this arrangement, the circulation resistance for the air that passes through the evaporator 1 is, compared to the circulation resistance from the first zone 1 'of evaporator 1, almost negligible and can disregard essentially for evaporator sizing 1 with a view to air circulation, so that unlike the basic variant of the evaporator without the cold storage zone 1 '', there is no need to perform or new calculations relevant with a view to air circulation. The flat tubes 6 and 7 may alternatively be arranged otherwise discretionary, for example aligned or in interstitium.

Flat tubes of cold storage 6 they have a double wall structure with a large number of 6 'refrigerant media channels and accumulator media channels 6 '' cold, 6 'refrigerant channels being arranged inside (see Fig. 8). At the same time the flat tubes of cold store 6 are arranged in such a way that the channels 6 '' cold storage media, which serve as elements 5 cold accumulators, end in each case in one of two collecting containers for cold storage medium 10, so that the cold accumulator element 5 has only a single hollow space which - regardless of a space of compensation - is completely filled with the accumulator medium of cold. Filling takes place through an opening in the 10 cold storage medium collector container in a single work process. After filling the opening is sealed from fixed form, so that an opening is not safely prevented authorized.

Inside the through hollow space are provided, according to a variant not shown in the drawing, elements such as, in the present case, a nonwoven material synthetic, which serve to improve heat transport as well as for the increase of the inner surface, in order to accelerate the formation of latent medium crystal.

6 'coolant channels protrude with its ends, in each case, through the containers corresponding cold accumulator media collectors 10 and ends, in each case, in a collecting container 12, formed separated from the collection vessel 9, formed in the present case as tube, to which reference will be made in what follows as collecting tubes.

Each of the collector tubes is connected in each case through a spill opening (not shown) oblong hole type with a spill opening 13 type oblong hole, arranged on the corresponding side, of the collecting containers 9 (see Fig. 5).

Evaporator 1 is crossed in such a way, in its conventional 1 'zone, that the coolant stream is deflected twice in the width of the evaporator before being deflected, in depth, against the direction of movement of the air. In the area of the air intake side it is also diverted twice wide. It is therefore an evaporator with six blocks B1 to B6, being provided every three blocks in the address of the width of the evaporator 1 (i.e. in the first row of blocks B1 to B3 crossed first and in the row of blocks B4 to B6 crossed last) and being traveled the individual blocks B1 to B6 of the two rows of cross blocks in counter current operation. This circulation route of the cooling medium is represented in Fig. 10 by Arrows with continuous line.

From the coolant stream is derived, through the spill opening 13 in the collection vessel 9, shortly after the injection tube 2 enters the container manifold 9 in the first block B1 a part of the cooling medium, which accesses through the spill opening in the tube collector and is distributed through the collector tube to the channels of cooling medium 6 'of the flat tubes 6, which in the in this case they are traveled in one direction, that is to say entire width of evaporator 1 in the accumulator zone of cold 1 '' there is only one block of accumulator element. The part derived from the cooling medium is supplied, through the spill opening, which is provided in the second tube manifold, and the corresponding spill opening 13 in the other collecting vessel 9 again then to the mainstream of cooling medium, which is diverted in this area of block B3 in depth towards block B4. The route of the circulation of cooling medium of the partial stream is represented in Fig. 10 by arrows with dashed lines.

Instead of the structure described above the collecting containers may also be structured in a different way, especially in a constructive way of plates.

In the remaining figures they are represented different variants of the conduction of cooling medium to through the cold storage zone 1 '' of evaporator 1, the which must ensure that the cold storage medium runs in all channels of cold storage medium 6 '' in the most uniform possible its phase change. To do this we must ensure that the partial current derived from the cooling medium is distributed  as uniformly as possible in flat tubes 6 with their 6 'cooling medium channels.

Figures 13a and 13b show a variant of connection with 3-block connection in the accumulator element. In In this case, the cooling medium is distributed, from each of the first three blocks B1 to B3 of the conventional zone 1 'of the evaporator 1 to the corresponding accumulator element block (it is say, that there are three blocks of accumulator element) and again of return. By the reduced number of connected parallel tubes in parallel per accumulator element block results a improved cooling medium distribution with respect to the example of embodiment described above.

According to a modification of this variant represented in the drawing are provided more than only one exit and entrance opening by block of the conventional zone of the evaporator, so that, for example, six are provided accumulator element blocks.

According to the second variant, represented in the Figures 14a and 14b, the conduction of the medium circulation refrigerant takes place in the accumulator element in correspondence with that of the serial evaporator (i.e. deviation twice in width). This connection is charged, in case of spillage, only once from the conventional zone 1 'of the evaporator 1, only one third of the flat tubes of the accumulator element in parallel with cooling medium. Other connections are also possible in the cold storage area 1 '', for example five element blocks can be provided accumulator.

Figures 15a and 15b show an entry direct cooling medium in the area of medium accumulator 1 '' refrigerant instead of conventional evaporator zone 1 ' 1. With this variant, a preferred supply can be guaranteed of the accumulator element block in the event that through the spill openings can be removed too little medium refrigerant from conventional zone 1 'of evaporator 1.

In Figures 16a and 16b it is foreseen, as fourth variant, a subdivided cooling medium inlet for the conventional zone 1 'of the evaporator 1 and the accumulator zone of cold 1 '', that is to say that the derivation of the partial current for the 1 '' cold storage zone takes place even before the refrigerant inlet in evaporator 1 in the area of injection tube At the same time, the medium distribution refrigerant to the two inlet openings can be optimized, in your case, through the diameter of the injection tube and the loss of pressure in the conventional zone 1 'of the evaporator 1 and in the zone of 1 '' cold store.

Figures 17a and 17b show a variant of connection with a serial connection of the cold storage zone 1 '' and, connected later, of the conventional zone 1 'of the evaporator 1. In this variant the medium is frozen first cold storage tank in the cold storage area 1 '' by means of the cooling medium current (in this case the inlet takes place from below), before the cooling medium then cross the zone 1 'in the usual current line conventional evaporator 1. Since all of the coolant stream is conducted completely through of the 1 '' cold storage zone, this variant is what freezes the cold storage medium faster.

In Figures 18a and 18b another one is represented connection variant according to which a current is derived again partial in the first block B1. The 1 '' cold storage zone at the same time it presents two blocks, the which are crossed in different directions. The middle refrigerant from the 1 '' cold storage zone goes out time in the collecting vessel of the third block B3 and what it crosses together, that is to say that the third block B3 is crossed by the entire cooling medium, while two first blocks B1 and B2 are crossed only by one cooling medium current (higher). The two blocks in the area 1 '' cold storage tank, according to the variant represented, a different width, the block being crossed in first place narrower than the block crossed later.

Connection variants make it possible to optimize an improved dynamics of the loading and unloading process and homogenize  the evaporator outlet temperature profile in case of shutdown of the motor vehicle.

All variants are independent of the medium refrigerant (R134a, R744), of the collector construction (folded collector, constructive form of plates) and the connection of series evaporator blocks (for example 2 or 4 connection blocks)

Claims (11)

1. Heat exchanger, in particular an evaporator (1), in particular for an air-conditioning installation of motor vehicles, with a plurality of pipes that conduct a cooling medium, located next to each other, and with at least one accumulator of cold (4), in which a cold accumulator medium is provided, characterized in that the evaporator (1) has two zones (1 'and 1'') arranged parallel to each other and extending along the whole of the width, the first zone (1 ') corresponding to its structure corresponding to a conventional evaporator, the cold accumulator (4) being arranged in a second independent zone (1''), which can be crossed by at least one part of the cooling medium stream, which also crosses at least a part of the first zone (1 ') and the first and second zones being connected to each other by at least one spill opening (13). 2. Heat exchanger according to claim 1, characterized in that two spill openings (13) are provided. 3. Heat exchanger according to claim 1 or 2, characterized in that at least one cold accumulator element (5) is arranged at least one tube that conducts a cooling medium. 4. Heat exchanger according to one of the preceding claims, characterized in that the tube that conducts a cooling medium and / or that contains a cold storage medium is a double-walled flat tube (6), the cooling medium being located in the central area and the cold storage medium in the outside area. 5. Heat exchanger according to one of the preceding claims, characterized in that the conductive tubes of a cooling medium of the second zone (1 '') end up in a collecting vessel (12), which is formed separately and connected only through one or more spill openings (13) with a collecting container (9) of the first zone (1 '). 6. Heat exchanger according to one of the preceding claims, characterized in that the pipes or channels leading a cold storage medium end up in a cold storage medium collecting container (10), through which the pipes or channels leading to it protrude a cooling medium, ending in a separate collection vessel (12). 7. Heat exchanger according to one of the preceding claims, characterized in that the first zone (1 ') has a number of blocks (B1 to B3), which can be crossed in different directions by the cooling medium, in the direction of its width contiguous to the second zone, and the second zone (2 '') has at least one block, in particular a number of blocks that can be crossed in different directions by the cooling medium, and the number and / or width of the blocks individual differs in the direction of the width of the evaporator (1) in the first zone (1 ') and in the second zone (1''). 8. Heat exchanger according to claim 7, characterized in that the first zone (1 ') has, directly adjacent to the second zone (1''), two to four, in particular three, blocks (B1 to B3), and The second zone (1 '') has one to six blocks, in particular two to four blocks. 9. Heat exchanger according to one of the preceding claims, characterized in that the phase change temperature of the cold storage medium is in a range between 0 ° C and 30 ° C, preferably between 1 ° C and 20 ° C, in particular between 2 ° C and 15 ° C, in particular preferably between 4 ° C and 12 ° C. 10. Heat exchanger according to one of the preceding claims, characterized in that at least one additional part is arranged in the cold accumulator (4). 11. Installation of air conditioning with a cold accumulator (4), in particular for a motor vehicle, with a cooling medium circuit, characterized in that it has an evaporator (1) according to one of claims 1 to 10.